Hydraulic transmission control



Jan. 29, .15546.

L. C. BLAIR HYDRAULIC TRANSMIS S ION CONTROL 5 sheets-sheet 1 Lyman @Bla/'T Filed Feb. 4, 1944 Jan. 2.9, 1946.

oec/euse' News 8.8M. Annow- 2 HYDRAULIC TRANSMI S S I ON CONTROL L. c. BLAIR 2,393,882

Filed Feb. 4, 1944 5 Sheets-Sheet 2 NCREASE E NGIN E R. P. M. ARROW-CZ,

OMA

- '27 Y 2g 26 SIMM?? 4411.29, 194e, y L. C. BLM 2,393,882

` HYDRAULIC TRANSMISSION CONTROL Filed Feb. 4, 1944 1 3 sheets-sheet s Lyman C; Blar Puentes Jan. as, 194s UNITED STATES PATENT OFFICE j l :sans: A

Appcatonlbfial'lrla. 521,088 11 Chim (mso- 19) This invention relates to hydraulic transmission control and more particularly to controls for hydraulic mechanism adapted for the transmitting of power from internal combustion engines to the driving elements, such as the wheels,

of automobiles, trucks, railway rolling stock and provide' stepless changes in the relative speeds of the pump and hydraulic motor driven thereby.

Another object is to provide a transmission mechanism of the character referred to in which, under ordinary or most conditions, the prime mover, e. g., internal combustion enginedriving the pump, may be operated at a selected substantially constant speed, which should be the speed at which the engine operates most eillciently, and to automatically vary the Iratio of engine speed to hydraulic motor speed to suit varying load conditions. I

Another object is to providey a novel and improved governor control for a transmission mechanism of the kind referred to.

March 6, 1945, as

A further object is to provide control means b for reducing the torque reaction on the engine in the event of a quick opening of the engine throttle valve so as to minimize or eliminate knocking such as otherwise would be apt to occur under such conditions.

Other objects will become apparent from` a reading of the following description, the appended claims, and the accompanying drawings, in

which Figure 1 is a somewhat diagrammatic plan view showing portions of amotor vehicle equipped with hydraulic transmission and control mechf anism embodying the invention;

Figure 2 is a fragmentary sectional view of a pump and control mechanism embodying the invention; y

Figure 3 is a detail view in vertical section showing a pulsation dampening chamber;

Figure 4 is a fragmentary section on the line 4-4 of Figure 2;

Figure' 5 is a fragmentary vertical section through a control motor armature and associated P6118;

Figure 6 is a fragmentary view looking in the direction oi' the arrow X in Figure 2 with some parts shown in section;

Figure 7 is a view, partially in elevation and partly in vertical section, of a governor for controlling the transmission mechanism shown in Figures 1 to 6 inclusive in dependence upon changes in the pressure inside the intake manifold of the internal combustion engine prime mover.

Pumps and transmissions constructed in accordance with the invention may be used for many purposes including the driving of vehicles, boats, and trains, the operation of hoists, cranes,

or other machinery. A preferred form of pump and transmission are shown as being designed and wheel assembly B. The engine is shown as including an intake manifold or pipe I and drive shaft 2. The rear axle assembly B inciudesthe usual drive shaft 3, dinerential gearing 4 andv driving wheels 5 5, The hydraulic transmission for delivering power from the engine shaft 2 to the wheels 5 includes a pump generally designated C and a hydraulic turbine or I'notor D arranged to be suppliedvwith working fluid under pressure delivered by a pump C through suitable pipes or conduits to be described.

In its more detailed nature the pump Cis sho as including two cylinders AS-Ii stationarily mounted on brackets 1-1 with their axes radial to the shaft I3. It will be understood that any desired number of radially disposed cylinders may be employed, although as a general rule a plurality of cylinders is desirable in the interest of smooth fluid delivery with minimum fluctuation in the discharge pressure. Reciprocally mounted in each of the cylinders 6 is a piston 8. A rotor generally designated 9 comprises a ilyA wheel I0 mounted on a web II provided with a hub II',`

'journaled in a fixed bearing I2. Fast to and roand the pistons 8 for reciprocating the latter consequent upon rotation of the rotor 8, the arrangement -being such that magnitude of piston strokes can be varied so as to control the pump output in a manner to maintain the speed of the engine A substantially constant at its optimum value,

at the top of Figure 2. The connecting rod 28 is formed with a clevis 2I jointed to a connecting rod 22 by a knuckle pin 28, the rod 22 in turn assasss pressure there will be backpressure exerted being connected in the usual manner to the piston 8 shown at the bottom in Figure 2. DuringI rotation of the rotor 8 with the pin I8 positioned eccentrically of the axis of rotation, the pistons 8 will be reciprocated in their associated cylinders 8, the length of their strokes being vdependent upon the degree of eccentricity of the crosshead pin I8.

Each cylinderv is provided at its outer end with an intake valve 24 adapted to control the admission of fluid through a pipe line 25 leadingto a reservoir 28 equipped with a breather cap 28". For controlling the delivery of fluid under pressure from the cylinders, the latter are provided with discharge valves 21 adapted to open during the outward strokes of the pistons 8 to'permit pressure fluid to flow through delivery pipes 28 into a thermally insulated pulsation dampening chamber 28 and thence through a pipe 88 and reversing valve 88'b to the turbine or nuid motor D coupled as aforesaid to the shaft 8 of the rear end assembly B, the shaft 8 constituting the driven element to which the hydraulic transmission delivers power. Fluid which is passed through the turbine or motor D ows through a vreturn pipe 82 and the reversing valve 38* tofthe receiver 28, thus completing the fluid circuit. In order to prevent the building up of excessive or unsafe pressures a reliefconduit 33 interposed between the high pressure conduit 38 and one low pressure conduit 28 is equipped with a pressure responsive overload or relief valve 34.

'I'he specific form of turbine or motor D does not form part of the present invention and any one of a number of well known hydraulic motors or turbines may be employed. The turbine D includes control levers 35'adapted to operate defiecting vanes (not shown) As has been indicated hereinabove, the eccentricity of the crosshead pin I8 determines the rate of discharge of the pump C. Mechanism is provided for changing the eccentricity of the pin I8 in response to deviations in the engine speed. The crosshead I8 has connected to it a rod 88 provided at its outer end with a crosshead-pin-positioning piston 31 reciprocally mounted in a crossheadpin-positioning cylinder 88 formed integrally with a ny wheel I8. The cylinder 88 is connected by piping 88 to the interior of the hollow shaft I8 which latter constitutes a servo cylinder in which is mounted a servo piston 48. The arrangement is such that when the piston 48 is moved in the direction of the arrow b in Figure V2, the uid 4I is forced -through the pipe 88 into the outer end of the cylinder 88 and against the piston 81 so as to move the latter inwardly toward `the axis of rotation and thereby move the crosshead I8 and crosshead pin I8 to an eccentric position such through the piston rodsv 28 and 22 tending to move the crosshead pin I8 to a concentric position. However, proper positioning ofthe piston 40 acting in opposition to the back pressure exerted through the piston rods-28 and 22 will maintain the crosshead pin in the desired eccentric position.

Power for moving the piston 48 for positioning the crosshead pin I8 is supplied by an electric motor 42 operated under the control of a governor generally designated 48. The motor 42 includes an armature 44 (see Figure 5) carried by a core or sleeve 45 which is internally threaded to mesh with the exterior threading on a supporting screw 48 mounted on bearing brackets 41. f Thrust bearings 48 are interposed between the ends of the armature sleeve 48 and the brackets 41. A slot 48 extending along the screw 48 receives tongues 58 extending inwardly from the bearing brackets. The arrangement is such that when the armature sleeve 48 is rotated. it is prevented by the bearings 48 and .brackets 41 from moving axially and consequently the screw 48 which is held against rotation by the slot 48 and tongue 88 will be moved longitudinally. Longitudinal movement of the screw in the direction of the arrow b in Figure 2 transmits thrust through a bearing 8l to a rod 48 connected to the piston 48 so as to move the latter in the direction of the arrow b and thus shift the crosshead pin I8 away from the axis of the shaft I3 in the manner previously described.

In accordance with the invention, mechanism of the kind thus far described may be equipped with governing means for maintaining the Ispeed of the engine A substantially constant at a selected value. Preferably this is accomplished by automatically increasing the rate of pump discharge in response to an increase in engine speed, thus increasing the torque reaction on the engine to slow it down, and conversely by decreasing the rate of pump discharge in response toa decrease in engine speed, thus reducing the torque and causing the engine to speed up.

As shown in Figures 1 and 2, a gear 82 meshing with the engine driven gear I8 is fast with a bevel gear 88 meshing with a bevel gear 84 which is fast with a governor yoke 88 journaled in a governor casing 88. The governor yoke mounts fly weights 81 which are urged to their inner positions as shown in Figure 2 by means of a spring 58 interposed between a thrust bearing 88 overlying the fly weight wings and a rack bar 88 which meshes with a pinion 8I rotatable by means of a control lever 82. lShifting of the lever 82 will raise or lower the rack bar 88 so as to decrease or increase the compression of the spring 88, thus decreasing or increasing the speed at which the governor will respond for effecting its control. Extending downwardly from the thrust bearing 59 and being slidable through the hub of the yoke 88 is a stem 88 equipped at its lower end with a grooved collar 84. One end of a switch lever asaa'aag l V3 the reversing mechanism is led to a battery 12 and thence thr/cgh a conductor 1I to the ground.

In operation and withthe crosshead pin Il at a given position of eccentricity, the engine A will continue to operate at the desired substantially constant speed until some change in the driving condltions'causesthe load either to increaseresulting in a tendency of the engine to slow down, or to decrease resulting in a tendency for the engine to increase in speed. If it -be supposed that the load increases and the engine speed decreases, the governor ily weights I1 will be moved inwardly by pressureV exerted by the spring 00,.

Y 31 to move outwardly in the cylinder and allow the crosshead l and pin i0 to, move toward a concentric position. The rate of pump discharge A' willbe-decreased more than in proportion tothe decrease oi thev engine speed. When the eccentricity of the crosshead pin l0 is reduced the remy-responsive to :sinn: or liquid level, or in the form shown, the valve 1B is carried by a Sylphon bellows actuator 10 which is iilled with gas under compression and is adapted to expand andclosethevalvewhenthepressureinthe chamber falls below a predetermined value. For the purposes of clear illustration the chamber 20 is shown somewhat removed from the cylinders. However in practice it is desirable that the chamber be. located as close as possible to the pump' cylinder or cylinders. In a multi-cylinder pump a separate pulsation dampening chamber may be-provided for each cylinder, each chamber being positioned adjacent the discharge valve of the associatedcylinder. Y

In order to maintain the rotor 0 and parts carried thereby substantially in balance, a very heavy iiuid ,may be used for transmitting movement from the piston I0 to the piston I1. By referring to Figures 2 and 6, it will be seen that when iluid is forced into thecylinder-ll, a movement torque reaction on the engine drive shaft 2 is lessened and the engine speed will increase until the governor responds to move the contact lever 05 out of engagement with the contact point 00. As soon as this has happened the motor 42 will cease operating and the crosshead pin I0 will be held in its new position of eccentricity until a further change in the load causes the governor to respond again.

If, however, the load should decrease, there would be a tendency for the engine A to increase its speed.l The governor would then respond to move the lever 05 into engagement with the contact point 01, completing a circuit through the conductor 1|, and causing the motor 42' to operate so as to move the screw 40, rod and piston 40 in the direction of the arrow b. Fluid forced by the piston 40 into the cylinder 38 would move the piston 31 inwardly so as to increase the eccenshown ascomprising a thermally insulated air tight casing with which the delivery pipes 28 and the pipe 30 communicate. An innation valve 14 at the top of the chamber is provided for introducing elastic iluid, for example air, under pressure. A normally open valve 15 provides for communication between the interior of the chamber and the pipe 30 under ordinary conditions.:

However, ii.' the vehicle should be coasting down a steep hill, there would be a tendency for the of the crosshead I0 to the eccentric position on one side of the axis of the rotor 0 will be accom panied by the introduction of an additional quantity of very heavy iluid into the outer end of the cylinder 00 and on the opposite side of the rotor axis. The additional heavy iluid has the eiIect of .compensating for the-shifting of the crosshead,

thus maintaining the rotor substantially bal-v anced.' Mercury,l which -has all the iiuid characteristics required for transmitting motion from the piston 40 to thejrpiston 01 and which also is very heavy, may be employed for this purpose.

Figure 'l shows a governor which may he used in place of the governor 43 shown in Figures 1 and 2 for responding to a sudden wide opening of the throttle valve of the engine A for decreasing the load on the engine and thereby preventing knocking. 'I'he governor shown in Figure 'I is generally designated |0| and includes a casing |02 on which is v,'Iournalled a rotary yoke |03 .equipped with a bevel gear |04 meshing with a is' interposed between thrust bearing |01 and a.

flexible corrugated disc-like diaphragm ||0. At its lower end the stem. |00 is equipped with a grooved collar which receives-one end of the contact lever 85 whose other end is cooperable with contact points 00 and 01 asin the embodiment shown'in Figures 1 and 2. 'I'he top ofthe governor casing |02 and the diaphragm III con- 'jointly deilne a chamber ||2 connected through a pipe H0 to the intake manifoldl of the engine A. a throttle valve ill being interposed in the manifold. f

In operation, with the engine A running at its selected speed and driving through the transmission under normal load conditions, a sudden turbine Dto run ahead of the pump C which v' might draw all of the pressure fluid out of. the' chamber 29 and permit the air orother exlpansible cushioning fluid to leak out of the chamber into the system piping. For preventing this, the valve 15 is arranged to be closed automatically in response to the falling of the pressure'iluid level inthe chamber 20 or the falling of the unit pressure in the chamber. This may be accomplished by any suitable device such as a float diopening of the throttle valve ||4 will result in a lessening of vacuum or4 stated differently, an increase in pressure in the manifold I and the chamber ||2. The diaphragm ||0 normally held slightly elevated by the vacuum in the chamber ||2, will then be pressed downwardly by the increased pressure and the resiliency of the diaphragm itseli'to cause the strut |09 to bear upon the thrust bearing |01 against the lifting urge of the ily weights |00, thereby lowering the stem |09 and causing the lever alto engage the contact point 08. As previously explained, such en gagement`will close' a circuit through the conductor 60 to the reversing mechanism I0 to eect operation of the motor 42 so as to move the screw 46, lrod 40', and piston 40 in the direction of the arrow 'a'in Figure 2. lThis will result inshifting ofthe .crosshead pin I 9 inwardly to a position of less eccentriclty, thereby decreasingA the torque reaction on the engine A and eliminating o'r minimizing knocking. The speed of the engine A will then increase so as to restore the normal vacuum, condition in the manifold I and governor chamber II2, after which the ily weights |06 will take over the predominant control of the eccentric position of the crosshead pin I9.

Although under ordinary or most conditions i the engine A will operate at a substantially constant speed selected as the engines most etiicient speed, it is intended that the throttle valve I I4 may be opened farther than usual tov increase the speed of the engine and the vehicle. Although thespeed ratio between the pump and motor would remain the same and the engine vopposition to response between the diaphragm and the governor, the arrangement being such that increased pressure in the manifold urges the diaphragm to act in ofthe governor to engine speed.

3. In combination, an internal combustion engine having an intake manifoldand throttle valve for controlling flow through saidy manifold; a pump; driving connections between the engine and pump; control means for varying the rate of pump delivery for a given engine speed: a

hydraulic motor; means for delivering fluid under pressure from said pump to said motor; a governor responsive to increase in engine speed for operating said control means to more than proportionately increase the the rate of discharge by the pump and responsive to decrease in engine speed for operating said control means to more than proportionately decrease the rate of discharge by the pump; and means responsive to quick opening of said throttle valve for tending to operate said control means to reduce the rate of pump discharge.

conductors 68 and 1|'. A bar III carried by the screw 46 is adapted to depress the button of and thusto open the switchA IIB when the screw retracts the piston 40 to a predetermined limit position. Similarly, when the screw has moved the piston 40 in the opposite direction to a predetermined limit position, the bar II'I will engage the button of the switch IIS, thereby opening the switch and stoppingA the motor 42. Thus the parts cannot be damaged by over-travelling of the screw 46 and piston 40.

Referring to Figure 2, the governor stem 63 may be extended downwardly at Ii3n into a dash pot |20 for reducing hunting of the governor control mechanism. In the form shown in Figure 7- the stem |08 is extended downward as at |08 into a dash pot I2 I.

The mechanism shown herein embodies the invention in the forms nowv preferred, but it will be understood that some changes may be made within the invention as defined by the claims.

I claim:

1. In combination, an internal combustion engine having an intake manifold; a pump; driving connections between the engine and pump; control means for varying the rate of pump delivery for a -given engine speed; a hydraulic motor; means for delivering fluid under -pressure from said pump to said motor; a governor responsive to increase in engine speed for operating said control means to more than proportionately increase the rate of discharge by the pump and responsive to decrease in engine speed for operating said control meansto more than proportionately decrease the rate of discharge by the pump; and means responsive to increased pressure in said manifold for tending to operate said control means to reduce the rate of pump discharge.

2. Combination as set iorth in claim l in which the means responsive to increased pressure in the manifold comprises a flexible diaphragm subjected to the manifold pressure and a connection 4. In combinationfan internal combustion engine having anjintake manifold; a pump; driving connections between theengine and pump; control means for varying the rate ofpump delivery for a given engine speed; a hydraulic motor; means for delivering fluid under pressure from said pump to said motor; a governor responsive to increase in engine` speed for operating said control means to increase the rate of dischange by the pump and responsive to decrease in engine speed for operating said control'means to decrease the rate of discharge by the pump; and means responsive to increased pressure in said manifold for tending to operate said control means to reduce the rate of pump discharge, and including a pressure responsive element subjected to the manifold pressure, and a connection between said element and said governor, the arrangement being such that increasedl pressure in the manifold urges said element to act in opposition to response of the governor to engine speed. v

5. In combination, an internal combustion en- ,gine having an intake manifold and throttle valve for controlling ow through said manifold; a

pump; driving connections between the engine and pump; control means for varying the rate of pump delivery for a given engine speed; a hydraulic motor; means for delivering fluid under pressure from said pump to said motor; a governor responsive to increase in engine speed for operating said control means to increase the rate of discharge by the pump-and responsive to decrease in engine speed for operating said control means to decrease the rate of discharge by the pump; and means responsive to quick opening of said throttle -valve for tending to operate said vcontrol means to reduce the rate of pump discharge.

6. In combination, an internal combustion engine having an intake manifold; a pump; driving 05' connections between the engine and pump; a'

hydraulic motor; means for delivering iluid under pressure from said pump to said motor; control means for varying the ratio between the fluid lcapacities of the pump and motor to thereby vary the driving speed ratio; a governor responsive to increase in engine speed for operating said control means to tend to increase the speed of the motor relative to the speed of the pump and responsive to decrease in engine speed for operating said control means to tend to decrease the ase'aesa speed of the motor relative to the speed vof the pump; and means responsive to increased pressure in 4said manifold tending to operate said control means to decrease the speed yof the motor relative to the speed of the pump.

'1. Combination as set`forth in claim 6 in which the means -responsive to increased pressure in.

the manifold comprises a flexible diaphragm sub- Jected to the manifold pressure and a connection between the diaphragm and the governor.

8. Combination as set forth in claim 6 in which the means responsive to increased pressure inlthe l manifold comprises a movable' element subjected to the manifold pressure and a 'connection between said element and the governor.,

9. In combination, an internal combustion enfor operating said control means to tend to de crease the speed of the motor relative to the pump; and means responsive to quick opening of said throttle valve for tending to operate s aid control means to decrease the speed of the motor relative to the speed of the pump.

10. In combination, a. prime mover; a pump;

driving connections -between the prime moverV and the pump; a hydraulic motor; means for delivering fluid under pressure from said pump to said motor; and control-means including a member movable for varying the ratio between the fluid. capacities of the pump and motor to v thereby vary the driving speed ratio, a hydraulic servo motor for operating said movable member, a reversible electric motor for operating said servo'motor, a switch for stopping said motor and for effecting operation thereof selectively in opposite directions, and a governor responsive to changes in the prime mover speed for actuating said switch. l

1l. In combination, an internal combustion engine having an intake manifold; a pump; driving connections between the engine and the pump; a hydraulic motor; means for delivering fluid under pressure from said pump to said hydraulic motor; and control means for varying the ratio between the fluid capacities of the pump and the hydraulic motor to thereby vary the drivingI speed ratio comprising a movable member, a hydraulic servo motor for operating said movable member, a reversible electric motor for operating said servo motor, a switch for stopping said electric motor and for effecting operation there of selectively in opposite directions, a governor responsive to increase in engine speed for operating said switch to effect operation of the elec-V tric motor in a direction to increase the ratio of the capacity of the pump to the capacity-of the hydraulic. motor and responsive to decrease in engine'speed for effecting operation of the electric motor in a direction to decrease the ratio of the capacity of the pump to the capacity of the hydraulic motor, and means responsive to increased pressure in said manifold for tending to operate said .control means to decrease the ratio of the capacity of the pump to the capacity or the hydraulic motor.

LYMAN C. BLAIR. 

